WO2015015960A1 - Dispositif de commande de synchronisation d'ouverture/fermeture de soupape - Google Patents

Dispositif de commande de synchronisation d'ouverture/fermeture de soupape Download PDF

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Publication number
WO2015015960A1
WO2015015960A1 PCT/JP2014/066854 JP2014066854W WO2015015960A1 WO 2015015960 A1 WO2015015960 A1 WO 2015015960A1 JP 2014066854 W JP2014066854 W JP 2014066854W WO 2015015960 A1 WO2015015960 A1 WO 2015015960A1
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WO
WIPO (PCT)
Prior art keywords
phase
fluid
intermediate lock
lock member
determination
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2014/066854
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English (en)
Japanese (ja)
Inventor
沼波晃志
岩屋崇
天野寛之
小林昌樹
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Priority to US14/772,144 priority Critical patent/US9726053B2/en
Priority to EP14832314.0A priority patent/EP3029286B1/fr
Priority to CN201480012253.9A priority patent/CN105026701B/zh
Publication of WO2015015960A1 publication Critical patent/WO2015015960A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/3443—Solenoid driven oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34463—Locking position intermediate between most retarded and most advanced positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34466—Locking means between driving and driven members with multiple locking devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34473—Lock movement perpendicular to camshaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2800/00—Methods of operation using a variable valve timing mechanism

Definitions

  • the present invention relates to a valve opening / closing timing control device that controls a relative rotation phase of a driven side rotating member that rotates integrally with a cam shaft of an internal combustion engine with respect to a driving side rotating member that rotates synchronously with a crankshaft of the internal combustion engine.
  • valve opening / closing timing control device that controls the opening / closing timing of one or both of an intake valve and an exhaust valve has been used in order to improve fuel consumption of an internal combustion engine (hereinafter referred to as “engine”).
  • engine an internal combustion engine
  • This type of valve opening / closing timing control device controls the opening / closing timing by changing the relative rotation phase between a driving side rotating member that rotates synchronously with the crankshaft and a driven side rotating member that rotates integrally with the camshaft.
  • the optimal opening and closing timing of the intake and exhaust valves varies depending on the engine operating conditions such as when the engine is started and when the vehicle is running.
  • the relative rotational phase of the driven side rotational member (hereinafter referred to as “relative rotational phase”) with respect to the rotation of the driving side rotational member is restricted to a predetermined phase between the most retarded angle phase and the most advanced angle phase.
  • This makes it possible to open and close the intake and exhaust valves that are optimal for starting the engine.
  • HC hydrocarbon
  • Patent Document 1 discloses a variable valve timing control device for an internal combustion engine having a function of locking a rotational phase of a camshaft with respect to a crankshaft of the internal combustion engine with an intermediate lock phase positioned substantially in the middle of the adjustable range.
  • the variable valve timing control device for an internal combustion engine includes a lock control means for controlling the hydraulic control device so that the rotation phase of the camshaft is locked at an intermediate lock phase by a lock pin when a lock request is generated.
  • the lock control means controls the hydraulic control device so that the rotation phase of the cam shaft passes the intermediate lock phase while urging the lock pin in the lock direction when a lock request is generated, and the cam shaft is controlled during this phase variable control.
  • the control amount of the hydraulic control device is further changed by a predetermined amount in the direction of moving the rotational phase of the camshaft. At this time, it is determined that the lock is completed when the rotational phase of the cam shaft does not move.
  • Patent Document 1 controls the rotational phase of the camshaft to pass the intermediate lock phase when a lock request is generated. Further, after the control, when the rotational phase of the cam shaft stops moving near the intermediate lock phase, the control amount of the hydraulic control device is further changed by a predetermined amount in the direction of moving the rotational phase of the cam shaft, and the rotational phase of the cam shaft is further changed. If it does not move, it is determined that the lock is complete. For this reason, the rotational phase of the camshaft may pass the intermediate lock phase, and in this case, it takes time to complete the lock.
  • an object of the present invention is to provide a valve opening / closing timing control device capable of quickly determining that an intermediate lock phase has been reached.
  • the characteristic configuration of the valve timing control apparatus includes a driving side rotating member that rotates synchronously with a crankshaft of an internal combustion engine, a camshaft of the internal combustion engine that rotates together with the driving side.
  • a driven-side rotating member that is rotatable relative to the rotating member; a fluid pressure chamber formed by the drive-side rotating member and the driven-side rotating member; and the fluid pressure chamber, the fluid pressure chamber being a fluid A retarding direction in which the volume of the retarding chamber is increased by the inflow of the fluid, and the relative rotation phase of the driven rotating member with respect to the driving rotating member is partitioned into a retarding chamber and an advance chamber allowing the inflow or discharge of And a vane that selectively moves between an advance angle direction in which the volume of the advance angle chamber increases due to the inflow of the fluid, and one of the drive side rotation member and the driven side rotation member, and the other Vs.
  • a locking member that is movable, and a recess that extends in a circumferential direction and is provided on one of the driving-side rotating member and the driven-side rotating member, and the locking member fits into the recess
  • a locked state in which the relative rotational phase is constrained to an intermediate lock phase between a most advanced angle phase and a most retarded angle phase, and an unlocked state in which the constraint is released by retracting the lock member from the recess.
  • An intermediate locking mechanism that can be switched to the medium, and supply of fluid to the retard chamber and discharge of fluid from the advance chamber, or from the retard chamber so that the lock member reaches the intermediate lock phase.
  • a phase control unit that controls discharge of fluid and supply of fluid to the advance chamber, and the phase control unit supplies fluid to the retard chamber and discharges fluid from the advance chamber; Fluid discharge from the corner chamber Then, after performing one control of the fluid supply to the advance chamber, the lock member is controlled to move toward a determination phase set at a position different from the intermediate lock phase in the recess. When the lock member reaches the determination phase, and when it is determined that the lock member has not reached the determination phase based on the determination result, the relative rotation phase is in the locked state. And a determination unit that determines that there is.
  • the lock member when the lock member is controlled to reach the intermediate lock phase in the state where the current position of the lock member, the intermediate lock phase, and the determination phase are arranged in this order as viewed from the current lock member position, If the lock member does not reach the determination phase in the determination operation (operation to move the relative rotation phase to the determination phase side), the lock member is in the intermediate lock phase (the relative rotation phase of the driven-side rotation member with respect to the drive-side rotation member is intermediate) It is possible to determine that it is a lock phase.
  • the lock member when the lock member is controlled so as to reach the intermediate lock phase in the state where the current position of the lock member, the determination phase, and the intermediate lock phase are arranged in this order as viewed from the current lock member position, the lock member Passes the determination phase, and if the determination phase is not reached again in the final determination operation, it can be determined that the lock member is in the intermediate lock phase.
  • the intermediate lock phase since the determination phase is provided at a position different from the intermediate lock phase in the recess, the intermediate lock phase is set when the relative rotational phase is shifted to the intermediate lock phase. It is possible to determine whether or not the lock member has reached the intermediate lock phase simply by controlling the target position (target phase) to be reached. Further, in the determination operation, it is only necessary to control the lock member so as to move to the determination phase side. Therefore, for example, the time for switching the control valve or the like can be shortened. Therefore, it can be quickly determined that the intermediate lock phase has been reached.
  • phase control unit is configured to supply the fluid to the retard chamber and discharge the fluid from the advance chamber, discharge the fluid from the retard chamber, and supply the fluid to the advance chamber.
  • the determination unit determines that the lock member has not reached the determination phase after performing one control, or when the determination unit determines whether the lock member reaches the determination phase, It is preferable to supply fluid alternately to each of the retard chamber and the advance chamber.
  • the determination phase is provided in any one of the two recesses, and one of the lock members is phased inside the corresponding recess.
  • the determination phase is set to a concave portion corresponding to a portion having a narrow restriction range with respect to the intermediate lock phase.
  • the determination phase can be set within a narrow regulation range, the interval between the determination phase and the intermediate lock phase can be narrowed. Therefore, it is possible to improve the determination accuracy of whether or not the relative rotation phase is the intermediate lock phase.
  • the length of one recess in the circumferential direction is shorter than the length of the other recess, and the determination phase is provided in the recess having a shorter circumferential length. It is.
  • the determination phase can be set within a narrow regulation range, the interval between the determination phase and the intermediate lock phase can be narrowed. Therefore, it is possible to improve the accuracy of determining whether or not the relative rotation phase is the intermediate lock phase.
  • the recess and the lock member are provided one by one, and the depth of the recess increases stepwise along the retardation direction, and the depth of the recess is deeper than other portions in the circumferential direction. Is preferably set so that displacement of the relative rotational phase of the driven-side rotator relative to the drive-side rotator is prohibited when the lock member is fitted into a deep recess.
  • the lock member when viewed from the current position of the lock member, the lock member is controlled so as to reach the intermediate lock phase in the state where the current position of the lock member, the intermediate lock phase, and the determination phase are arranged in this order. If the lock member does not reach the determination phase in the final determination operation, it can be determined that the lock member is in the intermediate lock phase.
  • the lock member when the lock member is controlled so as to reach the intermediate lock phase in the state where the current position of the lock member, the determination phase, and the intermediate lock phase are arranged in this order as viewed from the current lock member position, the lock member Passes the determination phase, and if the determination phase is not reached again in the final determination operation, it can be determined that the lock member is in the intermediate lock phase.
  • the concave portion and the lock member are provided one by one, and the length of the concave portion in the circumferential direction is a relative rotational phase of the driven side rotary body with respect to the driving side rotary body when the lock member is fitted into the concave portion. Is preferably set to be displaceable.
  • the lock member reaches the intermediate lock phase in the state where the current position of the lock member, the intermediate lock phase, and the determination phase are arranged in this order as viewed from the current position of the lock member.
  • the lock member passeses the determination phase, and if the determination phase is not reached again in the final determination operation, it can be determined that the lock member is in the intermediate lock phase.
  • FIG. 2 is a view showing a cross section in an unlocked state taken along line II-II in FIG. It is the figure which showed the cross section of the most retarded angle phase state in the II-II line of FIG. It is the figure which showed the intermediate
  • FIG. 1 is a side sectional view showing an overall configuration of a valve opening / closing timing control device 1 according to the present embodiment.
  • 2 to 4 are cross-sectional views of various states taken along line II-II in FIG.
  • the valve opening / closing timing control device 1 is mounted on a vehicle including an engine as the internal combustion engine E as a drive source, or a hybrid vehicle including a drive source including an engine and an electric motor.
  • the valve opening / closing timing control device 1 includes an external rotor 12 as a driving side rotating member and an internal rotor 2 as a driven side rotating member.
  • the external rotor 12 rotates synchronously with the crankshaft 110 of the internal combustion engine E.
  • the internal rotor 2 is arranged coaxially so as to rotate integrally with the cam shaft 101 of the internal combustion engine E and to be relatively rotatable with respect to the external rotor 12.
  • the valve opening / closing timing control device 1 controls the opening / closing timing of the intake valve 115 by setting the relative rotation phase (relative rotation angle) about the axis X of the external rotor 12 and the internal rotor 2. .
  • the inner rotor 2 is assembled integrally with the tip of the cam shaft 101. Specifically, the inner rotor 2 is fastened and fixed to the tip end portion of the camshaft 101 by fastening bolts 20.
  • a front plate 11, an external rotor 12, and a timing sprocket 15 that are provided on the side opposite to the side to which the cam shaft 101 is connected are integrally formed, and the cam shaft 101 is connected.
  • a rear plate 13 provided on the side.
  • the outer rotor 12 is externally mounted on the inner rotor 2 and is sandwiched between the front plate 11 and the rear plate 13 from both sides in the axial direction. In this state, the front plate 11, the external rotor 12, and the rear plate 13 are fastened and fixed by the fastening bolt 20 described above.
  • the outer rotor 12 is formed with a plurality of projecting portions 14 projecting radially inward and spaced apart from each other along the rotational direction S.
  • a pressure chamber 4 is formed.
  • the protruding portion 14 functions as a shoe for the outer peripheral surface 2 a of the inner rotor 2.
  • an example in which four fluid pressure chambers 4 are formed is described, but the present invention is not limited to this.
  • a vane groove 21 having a radial direction of the inner rotor 2 as a depth direction is formed in a portion of the outer peripheral surface 2a facing the fluid pressure chamber 4.
  • a part of the vane 22 is inserted into the vane groove 21 and is erected on the radially outer side. Accordingly, the vane 22 is disposed in the fluid pressure chamber 4.
  • the fluid pressure chamber 4 is partitioned by the vane 22 into an advance chamber 41 and a retard chamber 42 that allow inflow or discharge of oil along the rotation direction S.
  • the retard chamber 42 When oil is supplied to the retard chamber 42, the relative rotation phase of the inner rotor 2 with respect to the outer rotor 12 is moved (displaced) in the retard direction of the relative rotation direction.
  • the retarding direction is a direction in which the volume of the retarding chamber 42 increases due to the inflow of oil, and is the direction indicated by reference sign S2 in FIG.
  • the relative rotation phase is moved (displaced) in the advance direction of the relative rotation direction.
  • the advance angle direction is a direction in which the vane 22 rotates relative to the outer rotor 12 and the volume of the advance chamber 41 increases due to the inflow of oil, and is a direction indicated by reference sign S1 in FIG.
  • a spring 23 is disposed between the vane groove 21 and the vane 22, and the vane 22 is biased radially outward. As a result, oil leakage between the advance chamber 41 and the retard chamber 42 is prevented.
  • the vane 22 selectively moves the relative rotational phase between the retard direction and the advance direction.
  • an advance passage 43 is formed in the internal rotor 2 and the camshaft 101 so as to communicate with each advance chamber 41.
  • a retard passage 44 is formed in the internal rotor 2 and the cam shaft 101 so as to communicate with each retard chamber 42.
  • the advance passage 43 and the retard passage 44 are connected to a predetermined port of the first control valve 174.
  • a torsion spring 3 is provided across the inner rotor 2 and the front plate 11.
  • the torsion spring 3 biases the internal rotor 2 toward the advance side so as to resist the average displacement force in the retard direction S2 based on the torque fluctuation of the cam shaft 101.
  • the relative rotational phase can be displaced smoothly and quickly in the advance angle direction S1.
  • the inner rotor 2 can smoothly rotate relative to the outer rotor 12 around the axis X within a certain range.
  • a certain range in which the outer rotor 12 and the inner rotor 2 can move relative to each other, that is, the phase difference between the most advanced angle phase and the most retarded angle phase corresponds to the range in which the vane 22 can be displaced inside the fluid pressure chamber 4. To do. It is the most retarded phase that the volume of the retard chamber 42 is maximized, and the most advanced angle phase that the volume of the advance chamber 41 is maximized.
  • the intermediate lock mechanism 6 holds the outer rotor 12 and the inner rotor 2 at a predetermined relative position in a situation where the fluid pressure of the oil is not stable, such as immediately after the start of the internal combustion engine E, so that the outer rotor 12 and the inner rotor 2 are held.
  • the relative rotational phase of the phase is restricted to an intermediate lock phase between the most retarded angle phase and the most advanced angle phase.
  • the intermediate lock phase is the phase at which the valve opening timings of the intake valve 115 and the exhaust valve partially overlap (overlap), or the timing at which the exhaust valve closes and the intake valve 115 is opened.
  • the phase is almost the same as the timing (zero lap).
  • the opening timings of the intake valve 115 and the exhaust valve partially overlap, the hydrocarbon (HC) at the start of the internal combustion engine E is reduced, and the low emission internal combustion engine E is obtained. be able to.
  • the timing at which the exhaust valve is closed and the timing at which the intake valve 115 is opened are substantially the same, the internal combustion engine E having good startability and idling stability in the cold region can be obtained. .
  • the intermediate lock mechanism 6 includes an intermediate lock passage 61, two intermediate lock grooves 62, an accommodating portion 63, and two plate-like intermediate lock members 64. And a spring 65.
  • the intermediate lock groove 62 corresponds to the concave portion of the present invention
  • the intermediate lock member 64 corresponds to the lock member of the present invention.
  • the intermediate lock passage 61 is formed in the inner rotor 2 and the camshaft 101, and connects the intermediate lock groove 62 and the second control valve 175. By controlling the second control valve 175, the supply and discharge of oil to and from the intermediate lock groove 62 can be switched independently.
  • the intermediate lock groove 62 is formed on the outer peripheral surface 2a of the inner rotor 2 so as to extend in the circumferential direction, and has a certain width in the relative rotational direction.
  • the accommodating part 63 is formed in two places of the external rotor 12.
  • the two intermediate lock members 64 are disposed in the respective accommodating portions 63 and can be withdrawn and retracted from the accommodating portions 63 in the radial direction.
  • the intermediate locking member 64 is formed on the outer rotor 12 and is movable with respect to the inner rotor 2.
  • the spring 65 is disposed in the accommodating portion 63 and biases each intermediate lock member 64 radially inward, that is, toward the intermediate lock groove 62 side.
  • each of the two intermediate lock members 64 protrudes and fits into each of the intermediate lock grooves 62, whereby each intermediate lock member 64 is placed in a predetermined position of the intermediate lock groove 62. Will be locked at the same time.
  • the relative rotational phase of the inner rotor 2 with respect to the outer rotor 12 is constrained by the above-described intermediate lock phase.
  • a state in which the intermediate lock mechanism 6 restrains the relative rotational phase to the intermediate phase is referred to as a “lock state”.
  • a state in which the locked state is released is referred to as a “lock released state”.
  • the intermediate lock mechanism 6 is configured to be able to switch between such “locked state” and “unlocked state”.
  • a pin shape or the like can be appropriately employed in addition to the plate shape shown in the present embodiment.
  • the two intermediate lock grooves 62 are formed in a ratchet structure so that the groove depth increases stepwise along the retarding direction S2 in the inner rotor 2.
  • the intermediate lock member 64 is regulated in stages, and the intermediate lock member 64 can easily enter the intermediate lock groove 62.
  • the intermediate lock passage 61 is bifurcated in the middle of the inner rotor 2 and connected to each intermediate lock groove 62.
  • the valve opening / closing timing control device 1 includes a most retarded angle locking mechanism 7 in addition to the intermediate locking mechanism 6 described above.
  • the most retarded angle locking mechanism 7 holds the outer rotor 12 and the inner rotor 2 at a predetermined relative position during low speed rotation such as idling operation, thereby restraining the relative rotation phase to the most retarded angle phase. That is, since the internal rotor 2 does not move relative to each other regardless of the displacement force in the retard direction S2 and the advance direction S1 based on the torque fluctuation of the cam shaft 101, a stable idling operation state can be realized.
  • the most retarded angle phase is a phase that opens at a timing later than the closing timing of the exhaust valve, and avoids pre-ignition in the warm region of the internal combustion engine E while avoiding preignition. This is a phase that can ensure startability.
  • the most retarded angle locking mechanism 7 includes a most retarded angle lock passage 71, a most retarded angle lock groove 72, a housing portion 73, a plate-shaped most retarded angle lock member 74, and a spring 75.
  • the most retarded angle lock passage 71 is configured in combination with one of the plurality of advance angle passages 43.
  • the most retarded angle lock member 74 is the same member as the intermediate lock member 64 on the advance angle direction S1 side of the two intermediate lock members 64.
  • the accommodation portion 73 is the same as the accommodation portion 63 on the side of the advance direction S ⁇ b> 1 among the two accommodation portions 63
  • the spring 75 is the same as the spring 65 disposed in the accommodation portion 63.
  • the most retarded angle lock member 74 When the relative rotational phase is a phase other than the most retarded angle phase, the most retarded angle lock member 74 is displaced with respect to the most retarded angle lock groove 72 and therefore only makes sliding contact with the outer peripheral surface 2 a of the inner rotor 2. .
  • a pin shape or the like can be appropriately employed in addition to the plate shape shown in the present embodiment.
  • the most retarded lock member 74 (64) is the most retarded. It enters into the lock groove 72 and becomes the most retarded lock state.
  • the configuration can be simplified, the number of parts can be reduced, and the manufacturing cost can be reduced.
  • the intermediate lock member 64 and the most retarded angle lock member 74 are shared, there is a space in the outer rotor 12 in the circumferential direction, and four fluid pressure chambers 4 are provided as shown in FIG. it can.
  • the force for displacing the relative rotational phase is increased, and a rapid phase displacement can be realized. It is also possible to widen the circumferential range of the fluid pressure chamber 4 to widen the range in which the relative rotational phase can be displaced.
  • the hydraulic circuit includes a pump 171 that is driven by the internal combustion engine E to supply oil, a first control valve 174 that controls supply of oil to the fluid pressure chamber 4, and an intermediate lock.
  • a second control valve 175 that controls the supply of oil to the mechanism 6 is provided.
  • the phase control unit 180 controls the operation of the first control valve 174 and the second control valve 175 in order to control the above-described relative rotational phase.
  • the phase control unit 180 supplies the fluid to the retard chamber 42 and discharges the fluid from the advance chamber 41 or discharges the fluid from the retard chamber 42 so that the intermediate lock member 64 reaches the intermediate lock phase, for example. And the supply of fluid to the advance chamber 41 is controlled.
  • the phase control unit 180 uses an arithmetic processing unit, and may be composed of a single control device or a plurality of control devices.
  • the pump 171 is a mechanical hydraulic pump that is driven by the rotational force transmitted from the crankshaft 110 of the internal combustion engine E.
  • the pump 171 sucks oil stored in the oil pan 176 from the suction port, and discharges the oil downstream from the discharge port.
  • the discharge port of the pump 171 communicates with predetermined ports of the first control valve 174 and the second control valve 175.
  • the first control valve 174 can be, for example, a variable electromagnetic spool valve that displaces a spool that is slidably disposed in the sleeve by energizing the solenoid from the phase control unit 180 against the spring.
  • the first control valve 174 includes an advance port that communicates with the advance passage 43, a retard port that communicates with the retard passage 44, a supply port that communicates with a flow path downstream of the pump 171, and an oil pan 176. And a drain port communicating with the.
  • the first control valve 174 communicates the advance port with the supply port, advances the retard port with the drain port, communicates the retard port with the supply port, and connects the advance port with the drain port. It is composed of a three-position control valve capable of performing three state controls of angle control and hold control for closing the advance port and the retard port.
  • the advance angle control By performing the advance angle control, the vane 22 moves relative to the external rotor 12 in the advance angle direction S1, and the relative rotation phase is displaced toward the advance angle side.
  • the retard control is performed, the vane 22 relatively rotates in the retard direction S2 with respect to the external rotor 12, and the relative rotation phase is displaced to the retard side.
  • the hold control is performed, the vane 22 does not move relative to the rotation, and the relative rotation phase can be held at an arbitrary phase.
  • the first control valve 174 operates under the control of the phase control unit 180 and controls the supply or discharge of oil to the advance chamber 41 and the most retarded lock passage 71 or the retard chamber 42. As a result, the first control valve 174 performs switching control of the locked state or the released state of the intermediate lock mechanism 6 and control of the relative rotation phase of the internal rotor 2 with respect to the external rotor 12. In this embodiment, when the first control valve 174 is energized, the retard control can be performed, and when the power supply to the first control valve 174 is stopped, the advance control can be performed. The first control valve 174 sets the opening degree by adjusting the duty ratio of the power supplied to the electromagnetic solenoid. Thereby, fine adjustment of the supply and discharge amount of oil is possible.
  • the second control valve 175 is configured using a variable electromagnetic spool valve in the same manner as the first control valve 174.
  • the second control valve 175 has a restriction port that communicates with the intermediate lock passage 61, a supply port that communicates with the flow path on the downstream side of the pump 171, and a drain port that communicates with the oil pan 176.
  • the second control valve 175 is configured as a two-position control valve capable of performing two state controls: a release control that communicates the restriction port with the supply port, and a restriction control that communicates the restriction port with the drain port. .
  • the second control valve 175 operates under the control of the phase control unit 180 and controls the supply or discharge of oil to or from the intermediate lock groove 62 of the intermediate lock mechanism 6. In this manner, the second control valve 175 performs switching control of the restricted state or the released state of the intermediate lock mechanism 6.
  • the second control valve 175 can switch between oil supply to the intermediate lock groove 62 and oil discharge from the intermediate lock groove 62.
  • the second control valve 175 can discharge oil from the intermediate lock groove 62 when power is supplied, and can supply oil to the intermediate lock groove 62 when power supply is stopped. It is comprised so that it may be in a state.
  • a crank angle sensor for detecting the rotation angle of the crankshaft 110 is provided in the vicinity of the crankshaft 110 of the internal combustion engine E.
  • a cam shaft angle sensor that detects the rotation angle of the cam shaft 101 is provided in the vicinity of the cam shaft 101.
  • the phase control unit 180 detects the relative rotation phase from the detection results of the crank angle sensor and the cam shaft angle sensor, and determines which phase the relative rotation phase is in. Further, the ignition controller ON / OFF information and the like are transmitted to the phase controller 180.
  • optimal relative rotational phase control information corresponding to the operating state of the internal combustion engine E is stored in the memory of the phase control unit 180.
  • the phase control unit 180 controls the relative rotation phase according to the operating state of the internal combustion engine E.
  • the phase control unit 180 supplies the fluid to the retard chamber 42 and discharges the fluid from the advance chamber 41, discharges the fluid from the retard chamber 42, and discharges the fluid to the advance chamber 41.
  • the intermediate lock member 64 is controlled to move toward the determination phase set at a position different from the intermediate lock phase in the intermediate lock groove 62 after performing one control with the supply, the determination phase is changed to the determination phase. It is determined whether or not the intermediate lock member 64 has reached, and based on the determination result, when it is determined that the intermediate lock member 64 has not reached the determination phase, it is determined that the relative rotation phase is in the locked state.
  • One control of the fluid supply to the retard chamber 42 and the fluid discharge from the advance chamber 41 and the fluid discharge from the retard chamber 42 and the fluid supply to the advance chamber 41 is an intermediate lock.
  • hydraulic oil is supplied to and discharged from the advance chamber 41 and the retard chamber 42 so that the member 64 is in the intermediate lock phase.
  • FIG. 5 schematically shows the intermediate lock phase and the determination phase according to the present embodiment.
  • FIG. 5 shows a locked state in which the intermediate lock members 64 are respectively fitted in the intermediate lock grooves 62.
  • the position A where the intermediate lock member 64 exists in such a state corresponds to the position of the intermediate lock phase.
  • the position of the determination phase is set at a position different from such position A.
  • the position of such a determination phase is indicated with a symbol B.
  • the position of the determination phase is provided in one of the two intermediate lock grooves 62.
  • the determination phase is an intermediate lock corresponding to a portion having a narrow restriction range with respect to the intermediate lock phase.
  • the groove 62 is set.
  • the intermediate lock member 64 fitted in each of the intermediate lock grooves 62 is set in advance. Accordingly, the corresponding intermediate lock groove 62 corresponds to the intermediate lock groove 62 into which the predetermined intermediate lock member 64 is inserted when the relative rotational phase is the intermediate lock phase.
  • the restriction range with respect to the intermediate lock phase refers to a range in which the intermediate lock member 64 is movable in a state where the intermediate lock member 64 is fitted in the intermediate lock groove 62.
  • the intermediate lock groove 62 on the retarding direction S2 side corresponds to the range indicated by the symbol L1
  • the intermediate lock groove 62 on the advance angle direction S1 side corresponds to the range indicated by the symbol L2. Therefore, in the present embodiment, the intermediate lock groove 62 on the narrow side of the restriction range corresponds to the intermediate lock groove 62 on the advance angle direction S1 side.
  • the determination phase is set on the side of the end portion that is separated from the position A of the intermediate lock phase among the shallow depths in the intermediate lock groove 62 on the advance angle direction S1 side. More specifically, the determination phase is set at the center position in the circumferential direction of the intermediate lock member 64 when the intermediate lock member 64 is located at such an end.
  • the intermediate locking member 64 positioned at such an end is indicated by a two-dot chain line.
  • the intermediate lock member by the phase control unit 180 is used.
  • the determination unit 181 again turns the intermediate lock member 64 on the phase control unit 180.
  • the hydraulic oil is controlled to be supplied and discharged so as to rotate in the advance angle direction S1 (hereinafter referred to as “determination control”).
  • This determination control corresponds to the above-described “the intermediate lock member 64 is controlled to move toward the determination phase set at a position different from the intermediate lock phase in the intermediate lock groove 62”.
  • the determination unit 181 determines that the intermediate lock member 64 has reached the determination phase position B
  • the result is transmitted to the phase control unit 180.
  • the phase control unit 180 recognizes that the relative rotation phase of the inner rotor 2 with respect to the outer rotor 12 is not the intermediate lock phase (recognizes that the intermediate lock member 64 has passed the intermediate lock phase), and the phase control unit 180 performs the first control.
  • the valve 174 is controlled to rotate the inner rotor 2 in the retarding direction S2 to shift to the intermediate lock phase.
  • the phase control unit 180 recognizes that the relative rotation phase of the inner rotor 2 with respect to the outer rotor 12 is the intermediate lock phase, and the phase control unit 180 stops the control of the first control valve 174.
  • the intermediate by the phase control unit 180 is performed.
  • the determination unit 181 again instructs the intermediate lock member to the phase control unit 180.
  • the hydraulic fluid is controlled to be supplied and discharged (determination control is performed) so that 64 rotates in the advance direction S1.
  • the phase control unit 180 recognizes that the relative rotation phase of the internal rotor 2 with respect to the external rotor 12 is not the intermediate lock phase, and the phase control unit 180 controls the first control valve 174 to cause the internal rotor 2 to move in the retarding direction S2. To shift to the intermediate lock phase.
  • the phase control unit 180 recognizes that the relative rotation phase of the inner rotor 2 with respect to the outer rotor 12 is the intermediate lock phase, and the phase control unit 180 stops the control of the first control valve 174.
  • the above series of forms can be rephrased as follows.
  • the intermediate lock member 64 When viewed from the current position of the intermediate lock member 64, the intermediate lock member 64 is controlled so as to reach the intermediate lock phase in a state where the current position of the intermediate lock member 64, the intermediate lock phase, and the determination phase are arranged in this order. In this case, if the intermediate lock member 64 does not reach the determination phase in the final determination operation, it is determined that the intermediate lock member 64 is in the intermediate lock phase (the relative rotation phase of the internal rotor 2 with respect to the external rotor 12 is the intermediate lock phase). be able to.
  • the intermediate lock member 64 when viewed from the current position of the intermediate lock member 64, the intermediate lock member 64 is controlled so as to reach the intermediate lock phase in the state where the current position of the intermediate lock member 64, the determination phase, and the intermediate lock phase are arranged in this order. If the intermediate lock member 64 passes through the determination phase and does not reach the determination phase again in the final determination operation, it can be determined that the intermediate lock member 64 is in the intermediate lock phase.
  • the phase controller 180 supplies the fluid to the retard chamber 42 and discharges the fluid from the advance chamber 41, discharges the fluid from the retard chamber 42, and discharges the fluid to the advance chamber 41.
  • the determination unit 181 determines that the intermediate lock member 64 has not reached the determination phase after performing one control of supply, the fluid is alternately supplied to each of the retard chamber 42 and the advance chamber 41. Determination is made after one of the control of the supply of the fluid to the retard chamber 42 and the discharge of the fluid from the advance chamber 41 and the discharge of the fluid from the retard chamber 42 and the supply of the fluid to the advance chamber 41 are performed.
  • the case where the portion 181 determines that the intermediate lock member 64 has not reached the determination phase corresponds to the case where the intermediate lock member 64 is positioned at the intermediate lock phase.
  • the phase controller 180 since the relative rotation of the inner rotor 2 and the outer rotor 12 is restricted, the phase controller 180 alternately supplies fluid to each of the retard chamber 42 and the advance chamber 41, so that the relative rotation is performed.
  • the vane 22 In the restricted state, the vane 22 is swung in the advance angle direction S1 and the retard angle direction S2.
  • the intermediate lock member 64 does not reach the determination phase, it can be determined that the intermediate lock member 64 is securely fitted in the intermediate lock groove 62. Therefore, with this configuration, it is possible to confirm the fitted state of the intermediate lock member 64.
  • the hydraulic pressure in the passage connected to the retard chamber 42 and the advance chamber 41 is also increased / decreased. Can be removed (cleaned).
  • this valve opening / closing timing control device 1 since the determination phase is provided at a position different from the intermediate lock phase in the intermediate lock groove 62, when the relative rotational phase is shifted to the intermediate lock phase, It is possible to determine whether or not the intermediate lock member 64 has reached the intermediate lock phase simply by controlling the target position (target phase) to reach the intermediate lock phase. Further, in the determination operation, it is only necessary to control the intermediate lock member 64 so as to move to the determination phase side, so that the time required for switching the first control valve 174 can be shortened. Therefore, it can be quickly determined that the intermediate lock phase has been reached.
  • the determination phase is described as being set at the position B of the intermediate lock groove 62 on the advance angle direction S1 side in FIG.
  • the scope of application of the present invention is not limited to this.
  • the circumferential distance of the intermediate lock groove 62 on the retard angle direction S2 side is shorter than the circumferential distance of the intermediate lock groove 62 on the advance angle direction S1 side. (L1 ⁇ L2), it is naturally possible to set the determination phase at a predetermined position B on the advance angle direction S1 side in the intermediate lock groove 62 on the retard angle direction S2 side.
  • the two intermediate lock grooves 62 are described as being formed in a ratchet structure so that the groove depth gradually increases along the retarding direction S2 in the inner rotor 2.
  • the scope of application of the present invention is not limited to this.
  • the position A of the intermediate lock phase is provided at a predetermined position on the advance angle direction S1 side in the intermediate lock groove 62 on the advance angle direction S1 side, and is delayed on the intermediate lock groove 62 on the retard angle direction S2 side. It is provided at a predetermined position on the side of the angular direction S2.
  • the determination phase is the length in the circumferential direction. Is preferably provided within the short intermediate lock groove 62. Specifically, for example, as shown in FIG. 7, the circumferential distance of the intermediate lock groove 62 on the advance angle direction S1 side is larger than the circumferential distance of the intermediate lock groove 62 on the retard angle direction S2 side. If it is shorter (L1> L2), it is preferable to set the determination phase at a predetermined position B on the retard angle direction S2 side in the intermediate lock groove 62 on the advance angle direction S1 side.
  • the distance in the circumferential direction of the intermediate lock groove 62 on the retarded angle S2 side is shorter than the distance in the circumferential direction of the intermediate lock groove 62 on the advanced angle direction S1 side.
  • the intermediate lock groove 62 and the intermediate lock member 64 are provided one by one, and the intermediate lock groove 62 has a groove depth stepwise along the retarding direction S ⁇ b> 2 in the inner rotor 2. It may be formed with a ratchet structure so as to be deep. In such a case, the length on the side where the groove depth is deeper than the other parts in the circumferential direction is such that the outer rotor 12 and the inner rotor 2 do not rotate relative to each other when the intermediate lock member 64 is fitted into the deeper groove. It is preferable to set the degree. In other words, it is preferable to set so that the displacement of the relative rotational phase of the inner rotor 2 with respect to the outer rotor 12 is prohibited.
  • the intermediate lock groove 62 with a uniform groove depth.
  • the length of the intermediate lock groove 62 in the circumferential direction is such that the relative rotation between the outer rotor 12 and the inner rotor 2 can be permitted even when the intermediate lock member 64 is fitted into the intermediate lock groove 62. It is preferable to set. In other words, it is preferable to set so that the displacement of the relative rotational phase of the inner rotor 2 relative to the outer rotor 12 can be displaced.
  • the intermediate lock member is arranged in the order of the current position of the intermediate lock member 64, the intermediate lock phase, and the determination phase as viewed from the current position of the intermediate lock member 64.
  • 64 is controlled to reach the intermediate lock phase, if the intermediate lock member 64 does not reach the determination phase in the final determination operation, it can be determined that the intermediate lock member 64 is in the intermediate lock phase. Further, when viewed from the current position of the intermediate lock member 64, the intermediate lock member 64 is controlled so as to reach the intermediate lock phase in the state where the current position of the intermediate lock member 64, the determination phase, and the intermediate lock phase are arranged in this order.
  • the intermediate lock member 64 may be configured to be used together with the most retarded angle lock member 74 or may be configured separately.
  • the intermediate lock member 64 is provided in the outer rotor 12 and the intermediate lock groove 62 is provided in the inner rotor 2.
  • the scope of application of the present invention is not limited to this.
  • the intermediate lock member 64 may be provided in the inner rotor 2 and the intermediate lock groove 62 may be provided in the outer rotor 12.
  • the determination phase is described as being provided in one of the two intermediate lock grooves 62.
  • the scope of application of the present invention is not limited to this. It is also possible to configure so that the determination phase is provided in both of the two intermediate lock grooves 62.
  • the determination phase when the intermediate lock member 64 is in a state in which the phase change is restricted inside the intermediate lock groove 62, the determination phase is set to the intermediate lock groove 62 on the side where the restriction range with respect to the intermediate lock phase is narrow.
  • the determination phase can also be set to the intermediate lock groove 62 on the side where the restriction range relative to the intermediate lock phase is wide when the intermediate lock member 64 is in a state where the phase change is restricted inside the intermediate lock groove 62.
  • the phase control unit 180 supplies the fluid to the retard chamber 42 and discharges the fluid from the advance chamber 41, discharges the fluid from the retard chamber 42, and discharges the fluid to the advance chamber 41.
  • the determination unit 181 determines that the intermediate lock member 64 has not reached the determination phase after performing one control with supply, the fluid is alternately supplied to each of the retard chamber 42 and the advance chamber 41.
  • the first control valve 174 is one of the supply of the fluid to the retard chamber 42 and the discharge of the fluid from the advance chamber 41 and the discharge of the fluid from the retard chamber 42 and the supply of the fluid to the advance chamber 41.
  • the phase control unit 180 When the determination unit 181 determines that the intermediate lock member 64 has not reached the determination phase after the control is performed, the phase control unit 180 does not supply the fluid alternately to the retard chamber 42 and the advance chamber 41. Of course, it is also possible to configure. Further, the phase control unit 180 is configured to supply fluid alternately to each of the retard chamber 42 and the advance chamber 41 when the determination unit 181 determines whether or not the intermediate lock member 64 reaches the determination phase. Of course it is also possible.
  • the two intermediate lock grooves 62 are described as being formed in a ratchet structure so that the groove depth gradually increases along the retarding direction S2 in the inner rotor 2.
  • the scope of application of the present invention is not limited to this.
  • valve opening / closing timing control device 1 has been described with an example of controlling the opening / closing timing of the intake valve 115.
  • the scope of application of the present invention is not limited to this.
  • the valve opening / closing timing control device 1 may be configured to control the opening / closing timing of the exhaust valve.
  • the present invention is used for a valve opening / closing timing control device that controls a relative rotation phase of a driven side rotating member that rotates integrally with a cam shaft of an internal combustion engine with respect to a driving side rotating member that rotates synchronously with a crankshaft of the internal combustion engine. Is possible.
  • Valve opening / closing timing control device 2 Internal rotor (driven rotation member) 4: Fluid pressure chamber 6: Intermediate lock mechanism 12: External rotor (drive side rotating member) 22: vane 41: advance chamber 42: retard chamber 62: intermediate lock groove (concave) 64: Intermediate lock member (lock member) 101: Camshaft 110: Crankshaft 180: Phase control unit 181: Determination unit E: Internal combustion engine S1: Advance direction S2: Delay direction

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

La présente invention concerne un dispositif de commande de synchronisation d'ouverture/fermeture de soupape pouvant déterminer rapidement qu'une phase verrouillée intermédiaire a été atteinte, ledit dispositif de commande étant équipé de : un mécanisme de verrouillage intermédiaire pouvant commuter entre un état verrouillé, dans lequel un organe de verrouillage placé sur un organe rotatif du côté d'entraînement fait saillie et s'adapte dans un évidement placé sur un organe rotatif du côté entraîné, ce qui permet de bloquer la phase de rotation relative dans un état verrouillé intermédiaire, et un état déverrouillé, dans lequel l'organe de verrouillage se retire de l'évidement, ce qui permet de libérer le blocage ; une unité de commande de phase qui commande l'alimentation d'un fluide dans une chambre de retard et l'évacuation du fluide d'une chambre d'avance, ou commande l'évacuation du fluide de la chambre de retard et l'alimentation du fluide dans la chambre d'avance, de façon à permettre à l'organe de verrouillage d'atteindre la phase verrouillée intermédiaire ; et une unité de détermination qui, après l'exécution d'une commande par laquelle le fluide est alimenté dans la chambre de retard et le fluide est évacué de la chambre d'avance, ou par laquelle le fluide est évacué de la chambre de retard et le fluide est alimenté dans la chambre d'avance, et après que l'organe de verrouillage est commandé de façon à se déplacer vers une phase de détermination qui a été définie en une position différente de celle de la phase verrouillée intermédiaire dans l'évidement, détermine si l'organe de verrouillage a atteint la phase de détermination. Lorsque le résultat de la détermination est que l'organe de verrouillage n'a pas atteint la phase de détermination, l'unité de détermination détermine que la phase de rotation relative est dans l'état verrouillé.
PCT/JP2014/066854 2013-07-29 2014-06-25 Dispositif de commande de synchronisation d'ouverture/fermeture de soupape Ceased WO2015015960A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US14/772,144 US9726053B2 (en) 2013-07-29 2014-06-25 Valve opening/closing timing control device
EP14832314.0A EP3029286B1 (fr) 2013-07-29 2014-06-25 Dispositif de commande de synchronisation d'ouverture/fermeture de soupape
CN201480012253.9A CN105026701B (zh) 2013-07-29 2014-06-25 阀开闭时期控制装置

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JP2013-156936 2013-07-29
JP2013156936A JP5979093B2 (ja) 2013-07-29 2013-07-29 弁開閉時期制御装置

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JP6286044B2 (ja) * 2014-07-11 2018-02-28 本田技研工業株式会社 内燃機関の制御装置
JP6505579B2 (ja) * 2015-10-29 2019-04-24 株式会社Ｓｏｋｅｎ 可変バルブタイミング装置
JP6834658B2 (ja) * 2017-03-23 2021-02-24 アイシン精機株式会社 弁開閉時期制御装置
JP2019105167A (ja) * 2017-12-08 2019-06-27 アイシン精機株式会社 弁開閉時期制御装置

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JP2007132272A (ja) * 2005-11-10 2007-05-31 Aisin Seiki Co Ltd 弁開閉時期制御装置
JP2010138699A (ja) 2008-12-09 2010-06-24 Denso Corp 内燃機関の可変バルブタイミング制御装置
JP2010255499A (ja) * 2009-04-23 2010-11-11 Denso Corp 内燃機関の可変バルブタイミング制御装置
JP2011032905A (ja) * 2009-07-30 2011-02-17 Denso Corp 内燃機関の可変バルブタイミング制御装置
JP2011132932A (ja) * 2009-12-25 2011-07-07 Fuji Heavy Ind Ltd エンジンのバルブタイミング制御装置

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JP4000522B2 (ja) * 2003-02-26 2007-10-31 アイシン精機株式会社 弁開閉時期制御装置
JP4605473B2 (ja) * 2005-12-27 2011-01-05 アイシン精機株式会社 弁開閉時期制御装置
JP5240674B2 (ja) * 2009-05-12 2013-07-17 株式会社デンソー 内燃機関の可変バルブタイミング制御装置
JP4947499B2 (ja) * 2009-06-30 2012-06-06 株式会社デンソー 内燃機関の可変バルブタイミング制御装置
JP5141986B2 (ja) 2009-07-30 2013-02-13 株式会社デンソー 内燃機関の可変バルブタイミング制御装置
JP5321911B2 (ja) 2009-09-25 2013-10-23 アイシン精機株式会社 弁開閉時期制御装置

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Publication number Priority date Publication date Assignee Title
JP2007132272A (ja) * 2005-11-10 2007-05-31 Aisin Seiki Co Ltd 弁開閉時期制御装置
JP2010138699A (ja) 2008-12-09 2010-06-24 Denso Corp 内燃機関の可変バルブタイミング制御装置
JP2010255499A (ja) * 2009-04-23 2010-11-11 Denso Corp 内燃機関の可変バルブタイミング制御装置
JP2011032905A (ja) * 2009-07-30 2011-02-17 Denso Corp 内燃機関の可変バルブタイミング制御装置
JP2011132932A (ja) * 2009-12-25 2011-07-07 Fuji Heavy Ind Ltd エンジンのバルブタイミング制御装置

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CN105026701A (zh) 2015-11-04
US20160017767A1 (en) 2016-01-21
EP3029286A1 (fr) 2016-06-08
EP3029286B1 (fr) 2018-12-26
US9726053B2 (en) 2017-08-08
EP3029286A4 (fr) 2016-09-14
JP2015025440A (ja) 2015-02-05
JP5979093B2 (ja) 2016-08-24
CN105026701B (zh) 2017-10-20

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